Postage meter



Oct. 22, 1963 Filed ma 11,' 1962 I. H. LUNDQUIST ETAL POSTAGE METER 4Sheets-Sheet 1 IE'IE l Oct. 22, 1963 l. H. LUNDQUIST ETAL 3,107,911

' POSTAGE METER- Filed May 11, 1962 4 Sheets-Sheet 2 1953 l. H.LUNDQUIST ETAL' .POSTAGE METER 4 Sheets-sheaf. 3

Filed May 11, 1962 United States Patent 3,107,911 POSTAGE METER IngemarH. Lundquist, Oakland, and Willy Schaerer and Charles S. Balaz, Hayward,Califl, assignors to Friden, Inc., a corporation of California Filed May11, 1962, Ser. No. 194,124 14 Claims. (Cl. 271-3) This invention relatesto mail treating machines and more particularly to the envelope feedmechanism therefor. y

In the use of a mail treating machine, mail matter such as envelopes areconveyed past a printing station for a metered postmark impression to beapplied thereon. Where a considerable number of envelopes are to beprocessed, a stack of such envelopes is placed in a hopper on themachine and one-by-one the envelopes are separated from the stack fordelivery to the printing station. Such machines must be adaptable tohandle envelopes of various lengths and since those now in use aregeared to separate and convey the short envelopes in an expeditiousmanner, the processing of the longer envelopes is much slower due to theadditional time required to separate each of the longer envelopes fromthe stack. It is, therefore, an object of the present invention toprovide a mail treating machine with an improved envelope feed mechanismwhereby the speed of separation of each of the long envelopes isequivalent to that of each of the short envelopes.

Another object of the present invention is to provide an improvedenvelope feed mechanism for a mail treating machine by means of whichthe rate of separation of each envelope from a stack may be selectivelycontrolled in accordance with the length of the envelope.

Another object of the present invention is to provide a mail treatingmachine with means for automatically controlling the rate of separationof each envelope from a stack as determined by the length of theenvelopes.

A further object of the present invention is to provide a mail treatingmachine with an automatic speed control for the feeding of envelopes ofvarious lengths regulated by the length of the envelopes.

Other objects and advantages will be apparent from the followingdescription of a preferred embodiment as illustrated in the accompanyingdrawings in which:

FIG. 1 is a fragmentary elevational view of the front of the mailtreating machine.

FIG. 2 is a fragmentary elevational view of the front of the mailtreating machine complementary to FIG. 1 and having certain sections ofthe base portion broken away to show the speed control mechanism for theenvelope feed device.

FIG. 3 is a fragmentary sectional plan view of the base portion of themachine showing the envelope feed mechanism and the speed control drivemeans therefor with the drive means adjusted for the slower speed, theview being taken on the plane indicated by line 33 in FIG. 2.

FIG. 4 is a fragmentary sectional end elevational View of the baseportion of the machine showing the drive speed control mechanism for theenvelope feed mechanism, the view being taken on the planes indicated bythe lines 4-4 in FIG. 2.

FIG. 5 is a fragmentary sectional frontal elevational view of the baseportion of the machine showing the adjustable device for controlling thespeed of the envelope feed mechanism, the view being taken on the planeindicated by the line 5-5 in FIG. 4.

FIG. 6 is an enlarged plan view of the speed control mechanism and theadjustable means for enabling its operation, the view being taken on theplanes indicated by the lines 6-6 in FIG. 2.

FIG. 7 is an enlarged sectional elevational view showing Patented Oct.22, 1961s the pins associated with the larger of the driving pulleys andthe spider selectively engageable therewith for controlling itsoperation, the view being taken on the planes indicated by the lines 7-7in FIG. 6.

The invention is shown as being embodied in a mail treating, or postagemetering, machine of the type disclosed in the application of Ingemar H.Lundquist, Serial No. 801,594, filed March 24, 1959, utilizing theworkpiece feed mechanism of the type disclosed in Patent No. 3,074,532issued to Charles S. Balaz, January 22, 1963.

As illustrated, the mail treating machine comprises base portion 10,portable meter unit 12, super-structure 14 and workpiece separatingmechanism 16 (FIGS. 1 and 2). Within the base portion 10 is thepower-drive means in the form of an electric motor (not shown) whichserves to impart continuous movement to conveyer belt 20, as well as toprovide motivity to all the operational mechanisms of the machine. Theportable meter unit 12 is detachably mounted on the base portion 10 andincludes the postage indicia printing drum 21 rotatably supportedtherein, which, upon securing meter unit 12 in position on base portion10, is maintained in operative relation to conveyer belt 20. Followingthe securing of the meter unit 12 on the base portion 10, the operationof the meter unit, as well as the rotation of the indicia printing drum21, is efiected in a well-known manner by a cyclically operable drivemechanism within the housing of superstructure 14. Also driven by thecyclically operable drive means is the auxiliary, or town circle,printing drum, generally indicated at 22, the rotation of which is insynchronism with that of the indicia printing drum 21 and in timedrelation to the surface speed of the conveyer belt 20.

structurally, base portion 10 includes base plate 26, cover 27 andlongitudinally extending frame members 28, 29, 30 and 31 (FIGS. 2 and3). Each of the frame members 28, 30 and 31 is secured in position inany convenient manner between base plate 26 and the under side of thetop surface of cover 27, while frame member 29 is secured to the baseplate 26 and extends upwardly through a suitable aperture in cover 27.The extension of the frame member 29 above the cover is suificient toprovide a support for the separator device 16 and to serve as a guideagainst which one edge of the envelopes 32 is maintained during theseparation and feeding operation thereof. Edgewise uniformity of a stackof the envelopes 32 in hopper 33 is maintained by the laterallyadjustable plate 34 which is adaptable to maintain one edge of theenvelopes against guide plate 29.

In order to process the envelopes 32, they are removed one at a timefrom the hopper 33 and are fed in end-to-end fashion to conveyor belt29' for a simultaneous impression by each of the printing drums 21 and22. The removal of the envelopes from the stack is accomplished by meansof the feed mechanism, generally indicated at 38 (FIGS. 2 and 3), inco-operation with the separator device 16. Thereafter, each envelope ismoved into frictional engagement with the roller 39 of the auxiliaryfeed mechanism 40 (FIGS. 1 and 2), which is effective to continue themovement of the envelope into engagement with conveyer belt 20. Roller39' is driven by endless belt 41 and roller 42, which roller 42 isdriven frictionally by conveyer belt 20. The speed at which roller 39 isdriven is greater than the surface speed of the similar spaced parallelbelts 45 of the feed mechanism 38 and is less than the surface speed ofconveyer belt 20. Thus, as each envelope is frictionally engaged by theroller 39, its movement is immediately accelerated until it becomesfrictionally engaged with conveyer belt 20, whereupon its movement isaccelerated still more, thereby effecting a spaced relationship betweenthe trailing end of one envelope and the leading end of the adjacentenvelope.

Upon placing the stack of envelopes 32 into the hopper 33 (FIG. 2), theforward, or leading, edge of each envelope in the upper portion of thestack abuts the cover of the conventional separator unit 16, while theleading edge of each envelope in the lower portion of the stack abutsthe frictional wheels 46 of the separator 16. The leading edge of thelowermost envelope abutting the frictional wheels 46 is also in contactwith the frictional surface of the pair of feed belts 45, which beltsare continuously driven to successively effect a separation of thelowermost envelope from the stack of envelopes 32 and to feed theenvelopes in end-to-end fashion along the top surface of the cover 27 ofbase portion 10. In order to ensure sufficient frictional contact of theleading edge of the lowermost envelope with the top surface of the belts45, the stack of envelopes is positioned in the hopper 33 in angularrelationship to the top surface of the cover 27. The degree ofangularity of the stack of envelopes 32 relative to the top of the cover27 is determined by the inclined plate 48 of the gauge 47, adjustablysecured by means of the knurled nut and bolt 49 on the lateral extensionof the substantially vertically disposed hand grip 50 secured at itslower end on the slide 51. Slide 51 is in a form substantially that of achannel having each flange thereof formed angular-1y inwardly inconformity with the chamfered edge of the corresponding one of a pair ofsimilar bars 52 (FIGS. 3 and 4), upon which the slide 51 is slidablymounted. Bars 52 are preferably made of a thermoplastic material and aresupported in parallel spaced relationship on the horizontally disposedplate 54 by any suitable means, such as a plurality of screws 53, plate54 being suitably supported in any convenient manner between framemembers 36 and 31 in parallel relationship to the top of cover 27. Thus,it can be seen that the plate 48 may be adjusted relative to separatorunit 16 by moving slide 51 to the left or right (FIG. 2) on bars 52 toattain the required degree of angularity of the envelopes 32 inaccordance with the variation in the lengths of the envelopes to beprocessed.

The continuously operable workpiece, or letter, feed mechanism fordevices of the type described herein comprises the pair of similarendless belts 45, one of which is carried by a. pair of similar groovedpulleys 58 and 59 and the other of which is carried by a pair of similargrooved pulleys 60 and 61 (FIGS. 2 and 3). Pulleys 58 and 60 are coaxialand are secured in spaced relation on shaft 62 journalled in suitablebearings in frame members 30 and 31. Similarly, pulleys 59 and 61,having a diameter equivalent to pulleys 58 and 60*, are secured inspaced relation on the inner end portion of shaft 63 which is suitablyjournalled in bearings in each of frame members 30 and 31 in axialparallelism with shaft 62. The spacing between the pulleys 58 and 60 isequal to the spacing between pulleys 59 and 61, thereby providing aparallel relationship between the belts 4-5. As viewed from the right inFIG. 3, plleys 58 and 60 are axially displaced slightly to the right onshaft 62 out of alignment with the respective pulleys 59 and 61, therebycausing the parallel running belts 45 to run angularly inwardly towardthe vertically disposed guide plate 29. Thus, it can be seen that uponclockwise rotation of the pulleys 59 and 61, as viewed from below inFIG. 3, and upon the frictional engagement of the lowermost envelope ofthe stack of envelopes 32 with the belts 45, the one edge of thelowermost envelope will be retained in engagement with the vertical wallof guide plate 29, thereby ensuring true alignment of the envelopes asthey move in the feed path toward the printing station.

In addition to supplying power to the conveyer belt 20 and thecyclically operable drive mechanism for the indicia printing drum 21 andauxiliary printing drum 2-2, the electric motor (not shown) also servesto selectively drive the endless feed belts 45 at either of twoselective speeds. Power is transmitted from the motor to the endlessbelts 45 by means of drive shaft 68 (FiG. 3) and intermediate driveshaft 69, which serves to selectively impart rotation to shaft 63 (FIGS.2, 3, 4 and 6) by means of either toothed pulley 7t), timing belt 71 andtoothed pulley 72,

or by means. of toothed pulley 73, timing belt 74 and toothed pulley 75.Drive shaft 68 is journalled along its length in suitable hearings inbrackets 76 and 77 supported between frame members 28 and 29 and,adjacent its end, is adequately supported in spaced parallel cars 78 ofa bracket 79 secured on plate 80 supported between brackets 77 and 81.Shaft 69 is suitably journalled, adiacent one end, in a bearing in framemember 3 1 and, adjacent its other end, in a bushing in bracket 79', theshaft rotating freely in enlarged openings in frame members 29 and 30and plate 80. Continuous rotation of shaft 68 is transmitted to shaft 69by means of the worm and worm 7 gear unit, generally indicated at 82,the worm being secured on shaft 68 between cars 78 of bracket 79, andthe worm gear, enmeshed therewith, being secured on the end of shaft 69.Each of the toothed pulleys 70 and 73 is freely mounted in spacedrelationship on the other end of shaft 69, while the correspondingtoothed pulleys 72. and

'75 are secured in a similar spaced relationship on the outer end ofshaft 63. Normally, therefore, continuous rotation of shaft 69 is notimparted to shaft 63, but may be selectively utilized to eifectoperation of the endless belts 45, as will now be described. 7

In mail treating machines now in use and of the type in which thepresent invention is embodied, the workpiece, or envelope, feedmechanism operates at one speed, the maximum speed which is mostsatisfactory for the expeditious handling of short envelopes. Whenenvelopes of a longer dimension are to be processed, the time involvedin the separation of the envelopes from the stack becomesproportionately greater with the length of the envelope. In order toefiiciently handle the separation of envelopes, irrespective of thelength of the envelopes to be processed, the speed of the endless feedbelts 45 is selectively controlled.

For this purpose, the normal speed of the feed belts 45, i.e., the speedrequired for the efiicient separation of the short envelopes from thestack, is controlled by the selective connection of the toothed pulley70 with shaft 69, the pitch diameter of the pulley 70 being equivalentto that of the corresponding toothed pulley 72 (FIGS. 2, 4 and 6). Forthe separation of each envelope from a stack of longer envelopes, thespeed of the endless belts 45 is increased under the control of toothedpulley 73, the pitch diameter of which is greater than that of thecorresponding toothed pulley 75. The pitch diameter of pulleys 70, 72and 75 is identical. It becomes apparent, therefore, that shaft 63, whendriven by pulley 70, belt 71 and pulley 72, will rotate at the samespeed as shaft 69. However, if the rotation of the shaft 63 is under thecontrol of pulley 73, belt 74 and pulley 75, its speed will be greaterthan that of drive shaft 69.

As stated hereinbefore, the toothed pulleys 70 and 73 are freely mountedon shaft 69 and each is provided with a pair of disks 90, 91 and 92, 93,respectively, one for each side of, and secured on, the correspondingpulley. The diameter of each pair of disks 90, 91 and 92, 93 issufficiently greater than the outside diameter of the correspondingpulley to maintain the associated belts 71 and 74 in driving position onthe pulleys. Pulley 73 is positioned on shaft 69 adjacent the face offrame member 31 and is held against axial displacement by means of an Ering, or clip, engaged in an annular groove in the shaft. Similarly,pulley 70 is positioned on shaft 69, in spaced relationship to pulley73, and is held against axial dis,- placement on shaft 69 by means of apair of similar E rings, or clips engaged in corresponding annulargrooves in the shaft.

Either pulley 70' or 73 (FIGS. 4, 6 and 7) may be of three equiangularlyspaced pins 94 carried by disk 91 and projecting axially parallel to theshaft 69. Similarly, toothed pulley 73 is provided with a series ofthree equiangularly spaced pins 95 carried by disk 92 and project ingaxially parallel to shaft 69 and in opposition to the series of pins 94on pulley 70. Each series of pins 94 and 95 is disposed on the sameradius and is adaptable, respectively, for selective engagement by aclutch, generally indicated at 96, axially slidable upon shaft 69between toothed pulleys 70 and 73. Clutch 96 comprises a hub 100 on oneend of which a spider 101 is secured and on the other end of which asimilar spider -2 is secured in parallel relationship to spider 101(FIGS. 3, 4, 6 and 7). The three radially disposed arms of each spider101 and 102 are equiangularly spaced and are adapted for engagement withthe corresponding pins 94 on pulley 70 or pins 95 on pulley 73, uponaxial movement of clutch 96 to the right or left, as viewed in FIG. 4.In order to efifect rotation of either pulley 70 or 73, following theengagement of the arms of spiders 101 or 102 with the respective pins 94or 95, hub 100 is provided with a pair of diametrically opposed axiallyparallel keyways which are slida'bly engaged with the respectiveextended ends of a diametrically disposed pin 103 in shaft 69.

The overall width, or axial length, of clutch 96 is less than thedistance between the opposed ends of the series of pins 94 and 95 sothat, when the clutch is positioned in the area between the pins 94 and95 (FIG. 6), rotation of shaft 69 is ineffective to drive either pulley70 or 73. Normally, clutch 96 is maintained in this, the inactiveposition, by means of a manually controlled button 106 (FIGS. 2, 3, 6and 7) rockable about a vertically disposed pin 107 carried by a boss108 integrally for-med on base plate 26. The face of the control button106 projects through a suitable aperture in cover 27 so that it may beeasily rocked from the active position shown in FIG. 6 to the inactiveposition shown in FIG. 3. Button 106 is resiliently retained in eitherof its two positions by means of a toggle spring 109.

Upon rocking control button 106 counter-clockwise to the position shownin FIG. 6, a hook portion 110, integrally formed on button 106, engagesa roller 111 secured on the free end of one horizontally disposed arm112 of a bellcrank 115 pivotally mounted on a shoulder screw 116threaded into a boss 117 integrally formed on base plate 26 (FIG. 7). Inthis position of the button 106, a distention 118 (FIGS. 6 and 7),arcuately formed on each edge of the arm 112 intermediate its length andlying between the spiders 101 and 102 of the clutch 96 adjacent theperipheral surface of the hub 100, enables bellcrank 115 to maintain theclutch in its normally inactive position. To ensure positive adjustmentof the clutch 96, an arm 119 extends horizontally in spaced parallelrelationship to arm 112 integrally connected by web portion 120 tobellcrank 115. At its extremity, the arm 119 is provided with asubstantially circular end portion 121 lying between spiders 101 and 102adjacent the peripheral surface of the hub 100 of clutch 96 and indiametrical opposition to the distention 118 of arm 112.

The adjustment of the clutch 96 to either of its two active positionsbecomes automatic upon adjustment of the adjustable gauge 47 for theproper angular disposition of a stack of envelopes 32 within hopper 33,as determined by the length of the envelopes. It will be recalled thatsuch angular disposition of the envelopes in the hopper 33 is necessaryfor the separation of the envelopes one-by-one from the stack, uponoperation of endless feed belts 45. For what is preferably to beconsidered the normal speed of operation of the endless feed belts 45,i.e., for the separation and feeding of short envelopes, the gauge 47 isadjusted to the position shown in FIG. 2, adjusting slide 51 to theposition indicated in H6. 5, whereupon clutch 96 is moved to the activeposition shown in FIG. 4 to effect engagement of the arms 6 of spider101 with pins 94 on toothed pulley 70. An angle member, or actuator, 125is welded or otherwise secured on the lower surface and alongsubstantially the longitudinal center line of the channel slide 51,movable with the adjustment of the slide in the space between theparallel bars 52 (FIGS. 4 and 5).

Upon adjustment of the gauge 47, the angle member, or actuator, 125serves to control the selective adjustment of the clutch 96. For thispurpose, a 'bellcrank 126 (FIGS. 4, 5 and 6) is rockably mounted on ashaft 127 which is supported at its ends in frame members 30 and 31. Atits extremity, one arm of bellcrank 126 carries a roller 128 adapted forrolling contact with the lower edge of the vertically disposed leg ofangle member 125, while the other arm of bellcrank 126, at its free end,pivotally supports one end of a link 129 at 130. Link 129 extendshorizontally and, at its other end, is pivotally supported on a pin 131secured on the depending arm 132 of a bellcrank 133 roc-kably mounted ona shaft 134 supported at its respective ends in frame members 30 and 31axially parallel with shaft 127. An aperture in the other arm ofibellcrank 133', adjacent the end thereof, provides support for one endof a relatively strong spring 135 which is secured at its other end on apin 136 on auxiliary transverse frame member 137 secured in anyconvenient manner between frame members 30 and 31. spring 135 serves tourge bellcranks 133 and 126 in a clockwise direction to maintain roller128 in contact with the lower edge of the vertical leg of angle member125.

The rocking movement of the bellcranks 126 and 133, under control of theactuator 125, normally serves to control the rocking movement of thebellcrank 115 and the active adjustment of clutch 96 (FIGS. 5, 6 and 7).To this end, arm 132 of bellcrank 133 is provided, at its lowerextremity, with a pair of opposed arcuately formed lateral projectionsnormally, respectively, engaged with the laterally extended ears 138 and139, of the respective depending arms and 141 of a scissors-typeactuator, generally indicated at 1 42. Arms 140 and 141 are rockablymounted upon shaft 134, contiguous with each other and with bellcrank133, serving, upon rocking movement of bellcrank 133, to control therocking movement of bellcrank 115 and the adjustment of clutch 96. Forthis purpose, a relatively light spring 145, secured at its respectiveends on ears 138 and 139 of respective arms 149 and 141, normally servesto maintain the ears 138 and 139 in engagement with the respectiveprojections on the lower end of arm 132 of bellcrank 133. At the sametime, the inner parallel edge surfaces 147 and 148 of respective arms140 and 141 are maintained in'engagement with the parallel edge surfacesof the end portion of the horizontally disposed arm 146 formed at aright angle to am 112 of bellcrank 115. It is to be noted that spring145 provides a yieldable connection betwee arms 140 and 141 andbellcrank 115.

Referring to FIGS. 3 and 5, with the control button 106 rocked clockwiseto the inactive position shown in FIG. 3 and upon adjustment of thegauge 47 for the processing of short envelopes, slide 51 will beadjusted to the position shown in FIG. 5, wherein spring 135 urgesbellcrank 126 clockwise as the roller 128 moves upwardly along thebeveled end surface of the vertically disposed leg of the angle 125Accordingly, bellcra'nk 133 is effective to rock depending arm 140clockwise which, through spring 145, causes depending arm 141 to follow,thereby rocking bellcrank 1'15 (counter-clockwise in FIG. 3) to engagespider 101 of clutch 96 with pins 94 on toothed pulley 70. Thus, theendless belts 45 will be driven at a speed suitable for the eflicientseparation and feeding 7 7, whereupon bellcrank 1 15 is cammed in aclockwise direction to position clutch 96 intermediate pins 94 and 95.'Ihereupon, arm 141 of the scissors-type actuator 142 will be rockedcounter-clockwise (FIGS. and 7) causing spring 145 to yield, spring 135overcoming spring 145.

For the separation and feeding of the longer envelopes, gauge 47 and,therefore, slide 51 (FIGS. 2 and 5) are moved to the left, whereuponangle member 125 becomes efiective to rock :bellcranks 126 and 133counter-clockwise against the urgency of the spring 135. As bellcrank133 is rocked counter-clockwise, a similar rocking movement is impartedto the depending arm 141 which, through spring 145, causes a similarrocking movement of the arm 140 of the scissors-type actuator 142, whencontrol button 106 is in the inactive position shown in FIG. 3. Suchmovement of arms 141 and 140 causes bellcrank 115 to be rocked clockwise(FIG. 3) to engage the spider 102 of the clutch 96 with pins 95 on thelarger toothed pulley 73. Thereafter, the rotation of drive shaft 69causes feed belts 45 to be driven at an accelerated speed. Thetermination of the processing operation for the longer envelopes issimilar to that for the short envelopes except that, upon rockingmovement of the control button 106 to the active position shown in FIG.6, the depending arm 140 (-FIG. 5) is rocked clockwise, .tensioningspring 145. If, after the termination of an operation it becomesdesirable to again initiate processing of the long or short envelopes,control button 106 is rocked clockwise from the position shown in FIG. 6to the inactive position, whereupon spring 145 becomes effective torestore either the yieldable arm 140 or arm 141 to its active position,thereby adjusting clutch 96 in accordance with the setting of theadjustable gauge 47. If, upon initiation of a separating and feedingoperation for the short or long envelopes, clutch 96 should be out ofphase with either pins 94 on pulley 70 or pins 95 on pulley 73, theradial arms of spider 10 1 or 10-2 will engage the ends of thecorresponding pins 94 or 95 and spring 145 on the scissors-type actuator142 will yield. However, following a sufficient rotation of drive shaft69 and clutch 96, tensioned spring 145 will cause the radial arms ofeither spider 101 or 102 to be moved into active engagement with thecorresponding pins 94 or 95.

We claim:

1. In a workpiece separating and forwarding mechanism, a hopper for thestorage of a stack of workpieces, means for feeding the workpiecessingly from said hopper, a pair of normally inactive driving meansselectively operable to drive said feeding means at either of two ratesof speed, a power driven means adjustable for selec tive engagement witheither of said pair of driving means to control the operation thereof, amanually controlled means settable to bias said power driven means intoengagement with one or the other of said driving means, and amanipulable means operable to effect a disengagement of said powerdriven means from either of said driving means irrespective of thesetting of said settable means thereby terminating operation of saidfeeding means.

2. In a workpiece separating and forwarding mechanism, a feeding meansfor the workpieces, a separating abutment means associated with saidfeeding means for co-operation therewith to restrict the feeding tosingle workpieces from a stack of workpieces, a plurality of drivingmeans for said feeding means selectively operable to control the rate ofspeed of said feeding means, a continuously operable power driven meansincluding a clutch adjustable for selective engagement with each of saidplurality of driving means to control the speed of operation of saidfeeding means, and means settable to each of a plurality of positions tocontrol the selective adjustment of said clutch.

3. In a workpiece separating and forwarding mechanism, a hopper for thestorage of a stack of workpieces of one of each of a plurality oflengths, means for feeding the workpieces from said hopper, a separatingabutment means associated with said feeding means for cooperationtherewith to restrict the feeding to single workpieces from the stack ofworkpieces, means adjustable in accordance with the length of theworkpieces to maintain a uniform stack of workpieces in said hopper, aplurality of normally inactive means selectively operable to control thespeed of operation of said feeding means, a continuously operable drivemeans, a clutch driven by said drive means engageable selectively withone of each of said plurality of control means to drive said feedingmeans, means controlled by said adjustable means upon adjustment thereoffor effecting engagement of said clutch, and a manually settable meansfor controlling operation of said controlled means to effectdisengagement of said clutch irrespective of the adjustment of saidadjustable means thereby terminating operation of said feeding means.

4. In a workpiece separating and forwarding mechanism, a hopper for thestorage of a stack of workpieces, means for feeding the workpieces fromsaid hopper, a separating abutment means associated with said feedingmeans for co-operation therewith to restrict the feeding to singleworkpieces from the stack of workpieces, means adjustable relative tosaid separating abutment means for maintaining a uniform stack ofworkpieces in said hopper and for maintaining the lowermost workpiece inthe stack in feed relationship to said feeding means, a plurality ofdriving means, each operable selectively to control the speed ofoperation of said feeding means, a source of power, and means driven bysaid source of power adjustable by said adjustable means for engagementselectively with one of each of said driving means to control the rateof feed of said feeding means.

5. In a workpiece separating and forwarding mechanism, a hopper for thestorage of a stack of workpieces of one of each of a plurality oflengths, a variable speed means for feeding the workpieces from saidhopper, a

separating abutment means associated with said feed means forcooperation therewith to restrict the feeding to the successivelowermost workpiece from the stack of workpieces, means settable in eachof a plurality of positions relative to said separating abutment meansand in accordance with the length of the workpieces in said hopper tomaintain the lowermost workpiece in the stack in feed relationship tosaid :feed means, a plurality of driving means for said feed means, eachof said driving means being selectively operable to control a differentspeed of operation of said feed means, a power operated means, meansdriven by said power operated means adjustable to selectively controlthe operation of each of said driving means, and means actuated by saidsettable means upon movement to each set position thereof to control theadjustment of said adjustable means.

6. In a mail treating machine having a hopper for the storage of a stackof envelopes of one of each of various lengths, means for feeding theenvelopes from said hopper, a separating abutment means associated withsaid feeding means for co-operation therewith to restrict the feeding tosingle envelopes from the stack of envelopes, means manually adjustablerelative to said separating means in acordance with the length of theenvelopes in said hopper to maintain each successive envelope to be fedin frictional engagement with said feeding means, a power driven means,and a variable speed drive mechanism for controlling a selective rate ofspeed of said feeding means in accordance with the length of the en-.velopes in said hopper, the combination comprising a plurality ofindependent drive means for said feeding means, each of said drive meansbeing connectable selectively with said power driven means and operableupon operation thereof to effect a different rate of speed of operationof said feeding means, and means settable by said manually adjustablemeans for effecting a con- 9 nection between said power driven means andeach of said drive means to enable operation of a selected one of saidplurality of drive means as determined by the adjustment of saidadjustable means.

7. In a mail treating machine having means for controlling thesuccessive feeding of envelopes, a power driven means, and a variablespeed control mechanism interposed between said power driven means andsaid feeding means to regulate the speed of operation of said feedingmeans, the combination comprising a plurality of selective drive means,each operable upon selection thereof to drive said feeding means at adilferent rate of speed, means driven by said power driven meansconnectable selectively with one of said drive means, a manuallyadjustable means, means controlled by said manually adjustable meansoperable to bias said connectable means into operative relation with aselected one of said drive means, and a manually settable meansadjustable from an inactive to an active position to disable saidbiasing means disconnecting said connectable means thereby terminatingoperation of said feeding means.

8. In a mail treating machine having a hopper for the storage of a stackof envelopes of one of each of various lengths, endless belt means forfeeding the envelopes from said hopper, a separating abutment meansassociated with said endless belt means for co-operation therewith torestrict the feeding to single envelopes from the stack of envelopes, agauge adjustable relative to said separating means in accordance withthe length of the envelopes in said hopper to maintain each successiveenvelope to be fed in frictional engagement with said endless belt meansa continuously operable drive means for said endless belt means, and avariable speed mechanism interposed between said drive means and saidendless belt means for regualting the speed of operation of said endlessbelt means, the combination comprising a plurality of power transmissionmeans, each operable selectively to drive said endlessbelt means at adifferent rate of speed in accordance with the length of the envelopesin said hopper, means driven by said drive means adjustable for drivingengagement selectively with each of said power transmission means,engaging means for effecting the engagement of said driven means withone of said power transmission means, and means settable by said gaugefor controlling the operation of said engaging means in accordance withthe adjustment of said gauge.

9. In a mail treating machine having a hopper for the storage of a stackof envelopes of either of two lengths, an endless feed belt for feedingthe envelopes from said hopper, a separating abutment means associatedwith said endless belt for co-operation therewith to restrict thefeeding to single envelopes from a stack of envelopes, a gauge manuallyadjustable relative to said separating means in accordance with thelength of the envelopes in said hopper to maintain each successiveenvelope to be fed in frictional engagement with said endless belt, acontinuously operable drive means including a shaft, and a variablespeed control mechanism for controlling operation of said endless belt,the combination comprising a pair of power transmission means, eachselectively operable to drive said endless belt at a different rate ofspeed, a clutch means supported on said shaft and adjustable for drivingengagement with either of said power transmission means to effectoperation thereof by said drive means, means associated with said clutchmeans rockable to either of two positions to control the adjustment ofsaid clutch means, and means settable by said gauge upon each adjustmentthereof effective to control the positioning of said rockable means.

10. In a device of the character described in claim 9', said powertransmission means comprising a pair of similar driven means associatedwith said endless belt in spaced relationship for enabling the operationof said belt and a pair of driving means freely mounted for in dependentactuation on said shaft and spaced thereon in accordance with thespacing between said driven means for controlling operation of saiddriven means, one of said driving means being operable upon engagementof said clutch means therewith to drive the corresponding one of saiddriven means at a given speed and the other of said driving means beingoperable upon engagement of said clutch means therewith to drive theother of said driven means at a greater speed.

'11. In a device of the character described in claim 10, wherein each ofsaid driving means includes a similar series of pins secured ineq-uiangularly spaced relationship thereon axially parallel to saidshaft'and in opposition, one series to the other for selective drivingengagement by said clutch means.

12. In a device of the character described in claim 11, said clutchmeans comprising a member keyed for axial sliding movement on said shaftbetween each of said i riving means, and a pair of spiders secured inspace-d relationship on said member for sliding movement therewith andpositionable between the opposed ends of said pins on each of saiddriving means, each of said spiders including a series of radiallydisposed arms adapted for engagement with the series of pins on thecorresponding one of said driving means upon adjustment of said memherby said rockable means.

13. In a device of the character described in claim 12, including amanually operable means selectively adjust,- able from an inactive to anactive position to rock the rockable means for controlling the slidingmovement of said member and the inactive positioning of said spidersrelative to the series of pins on each of said driving meansirrespective of the setting of said settable means by said gauge,thereby terminating operation of said driving means.

14. In a device ofthe character described in claim 13,

means to the active position to enable the inactive positioning of saidmember in either adjusted position of said gauge.

No references cited.

1. IN A WORKPIECE SEPARATING AND FORWARDING MECHANISM, A HOPPER FOR THESTORAGE OF A STACK OF WORKPIECES, MEANS FOR FEEDING THE WORKPIECESSINGLY FROM SAID HOPPER, A PAIR OF NORMALLY INACTIVE DRIVING MEANSSELECTIVELY OPERABLE TO DRIVE SAID FEEDING MEANS AT EITHER OF TWO RATESOF SPEED, A POWER DRIVEN MEANS ADJUSTABLE FOR SELECTIVE ENGAGEMENT WITHEITHER OF SAID PAIR OF DRIVING MEANS TO CONTROL THE OPERATION THEREOF, AMANUALLY CONTROLLED